JP3555360B2 - Toroidal type continuously variable transmission - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a mechanism for equalizing a transmission torque in a toroidal type continuously variable transmission used for an automobile or the like.
[0002]
2. Description of the Related Art Toroidal-type continuously variable transmissions use a power roller with a large force between input and output disks as disclosed in Japanese Patent Application Laid-Open Nos. Sho 56-108947 and 58-54262. Pressing and powering by shearing the oil slick during that time. The force acting upon power transmission is proportional to the difference vector between the speed vector of the disk and the power roller at the contact point. The speed change is performed by changing the radius ratio of the input / output disk at the contact point by tilting the power roller. The power roller is rotatably supported by a roller support member in a state where the power roller can also tilt. The roller supporting member has a structure capable of being displaced in the axial direction by a hydraulic cylinder device.
[0003]
The hydraulic pressure of the hydraulic cylinder device is controlled by a shift control valve. The speed change control valve has a sleeve and a spool fitted in a state in which they can move relative to each other. The position of one of the sleeve and the spool is controlled by an actuator such as a step motor in accordance with a target gear ratio obtained by a controller of a gear change control device, and the other is in accordance with the tilt angle (gear ratio) of the roller support member. The position is determined by a cam connected to the roller support member. Here, in order to ensure the contact between the cam and the shift control valve, one of the shift control valves is pressed against the cam by a spring.
[0004]
The toroidal type continuously variable transmission is configured to have a plurality of power rollers in order to increase a transmission torque capacity. For example, a double cavity type having two sets of input / output disks, and two power rollers are provided in each cavity. Those having a total of four are common.
[0005]
Even if a plurality of power rollers are provided, the precess cam is connected to only one of them, and the tilt angle and axial displacement of the power roller are mechanically fed back to the transmission control valve. To control the tilt angle.
In other words, the control oil pressure is applied not only to the power roller to which the precess cam is connected but also to the remaining power rollers. That is, a common control pressure acts on the hydraulic cylinder device that drives each power roller, and each power roller transmits a torque that matches the control pressure, so that the transmission torques are all equal.
[0006]
However, in such a toroidal type continuously variable transmission, as described above, in order to secure the connection between the cam mechanism and the shift control valve, It is structured to preload using a spring. A reaction force always acts on the support mechanism with the cam due to the preload by the spring. That is, while the control pressure + spring force acts on the support mechanism with the cam, only the control pressure acts on the remaining support mechanisms, so that imbalance occurs in torque sharing.
[0007]
This imbalance in torque sharing causes a slight difference in the tilt angle for each power roller, and generates and absorbs a difference in the slip ratio at the point of contact with the input / output disk. That is, when the transmission torque is positive, the power roller having a large torque share slightly tilts toward the gear ratio Hi where the slip ratio increases, and the traction coefficient increases by that amount, and the traction force increases with the same pressing force. Which balances with the piston differential pressure + spring force.
Conversely, a power roller with a small torque distribution slightly tilts to the gear ratio Low side where the slip ratio is small, and the traction coefficient is reduced accordingly, and a smaller traction force is generated with an equal pressing force, and this is Balance with pressure.
[0008]
By the way, the pressing force in the toroidal type continuously variable transmission has a characteristic as shown in FIG. 6 due to a disc spring that generates a constant force and a loading cam that generates a pressing force proportional to the input torque. The traction coefficient at the contact point is set to a constant value in a region where the operation is performed by the pressing force of the loading cam, and is referred to as a design traction coefficient. Therefore, the value becomes smaller than the traction coefficient at the time of operation, and the margin increases.)
The design traction coefficient is determined in consideration of a margin from a maximum value of the traction coefficient determined from the characteristics of the traction oil at the contact point. If the design traction coefficient is too large, the margin until slippage becomes small, and if it is too small, the pressing force must be set large, which increases the friction of the rotating member and deteriorates the efficiency. Therefore, usually, a design traction coefficient is set to be as large as possible with some allowance.
[0009]
However, when the imbalance in torque sharing as described above occurs, it is necessary to design based on the contact point that is sharing the most torque, that is, operating with the largest traction coefficient. The largest imbalance in torque sharing occurs when the operation is performed around the time when the pressing force changes from the disc spring to the loading cam (around the circle shown in FIG. 6). This is because the ratio of the magnitude of the spring force to the magnitude of the traction force at the contact point is maximized. Therefore, in order to secure a certain margin, it is necessary to at least increase the force of the disc spring (in order to make it more perfect, the design traction coefficient of the loading cam also needs to be slightly reduced). However, these have a problem that the efficiency of the transmission is deteriorated.
The present invention has been made in order to solve such a conventional problem, and an object of the present invention is to achieve a uniform transmission torque without deteriorating the efficiency of a transmission. It is to provide a step transmission.
[0010]
In order to achieve the above object, a toroidal type continuously variable transmission according to the present invention comprises:
(1) By providing a preload canceling means for applying a force equivalent to a preload mechanism for connecting the cam mechanism and the shift control valve to the power roller supporting member to which the precess cam is not connected, all the power rollers are provided. By equalizing the force acting on the support member, the torque sharing of each power roller is equalized.
(2) The power roller support member to which the precess cam is connected is provided with a pre-pressure canceling means for generating a force in the opposite direction, which is substantially equal to the pre-load mechanism for connecting the cam mechanism and the speed change control valve, and This counterbalances the reaction force and equalizes the torque distribution of each power roller.
[0011]
Embodiments of the present invention will be described below in detail with reference to the drawings. FIG. 1 shows a toroidal type continuously variable transmission according to the present embodiment, and FIG. 2 shows a cross section thereof.
In the toroidal type continuously variable transmission 10 shown in FIG. 1, the rotation of an unillustrated engine as a power source provided on the left side in the figure is input to the toroidal type continuously variable transmission 10 via the torque converter 12. It has become.
The torque converter 12 is generally well known, and includes a pump impeller 12a, a turbine runner 12b, and a stator 12c. In particular, the torque converter 12 is provided with a lock-up clutch 12d.
[0012]
The toroidal type continuously variable transmission 10 is provided with a torque transmission shaft 16 disposed coaxially with the output rotation shaft 14 of the torque converter 12, and the first toroidal transmission unit 18 and the The two toroidal transmission units 20 are arranged in tandem.
The torque transmission shaft 16 is formed to be hollow, and is attached to the housing 22 so as to be able to move slightly in the axial direction.
[0013]
The first and second toroidal transmission portions 18 and 20 each include a pair of first input disk 18a, first output disk 18b, second input disk 20a, and second output disk 20b each having a facing surface formed into a toroidal curved surface. And power rollers 18c, 18d and 20c, 20d that are brought into frictional contact between respective opposing surfaces.
[0014]
The first toroidal transmission portion 18 is disposed on the left side of the torque transmission shaft 16 in the drawing, and the second toroidal transmission portion 20 is disposed on the right side of the torque transmission shaft 16 in the drawing. The first input disk 18a and the second input disk 20a are arranged outside each other, and the first output disk 18b and the second output disk 20b are arranged inside each other.
The first and second input disks 18a and 20a are fixed to the torque transmitting shaft 16 via ball splines 24 and 26 in the rotational direction and mounted so as to be able to smoothly move in the axial direction.
[0015]
On the other hand, the first and second output disks 18b and 20b are spline-fitted to an output gear 28 rotatably fitted to the torque transmission shaft 16, and are fitted to the first and second output disks 18b and 20b. The transmitted torque is transmitted to the counter shaft 30 via the output gear 28 and the input gear 30a meshed with the output gear 28, and further transmitted to an output shaft (not shown) via a torque output path.
[0016]
By the way, a loading cam device 34 is provided outside the first input disk 18a, and the engine rotation transmitted through a torque input path is input to the loading cam device 34 according to the input torque. The pressing force is generated by the loading cam device 34.
The loading cam 34a of the loading cam device 34 is rotatably fitted to the torque transmission shaft 16 and is locked to the torque transmission shaft 16 via a thrust bearing 36.
[0017]
A disc spring 38 is provided between the second input disk 20a and the right end of the torque transmission shaft 16 in the drawing.
Therefore, the pressing force generated by the loading cam device 34 acts on the first input disk 18a, and also acts on the second input disk 20a via the torque transmission shaft 16 and the disc spring 38, and The preload generated by the disc spring 38 acts on the second input disc 20a and also acts on the first input disc 18a via the torque transmission shaft 16 and the loading cam device 34.
[0018]
By the way, a forward / reverse switching device 40 that switches the rotation direction between when the vehicle moves forward and when the vehicle moves backward is provided on the torque input path between the loading cam device 34 and the torque converter 12.
The forward / reverse switching device 40 includes a planetary gear mechanism 42 of a double planetary system, a forward clutch 44 capable of fastening a carrier 42 a of the planetary gear mechanism 42 to the output rotary shaft 14, and a ring gear of the planetary gear mechanism 42. 42b is constituted by a reverse brake 46 which can be fastened to the housing 22.
[0019]
In the forward / reverse switching device 40, by engaging the forward clutch 44 and releasing the reverse brake 46, rotation in the same direction as the engine rotation is input to the loading cam device 34, and the forward clutch 44 By releasing and engaging the reverse brake 46, rotation in the reverse direction is input.
In the planetary gear mechanism 42, reference numeral 42c denotes a sun gear, and reference numerals 42d and 42e denote planetary gears meshed with each other.
[0020]
By the way, the power rollers 18c, 18d and 20c, 20d provided in the first toroidal transmission unit 18 and the second toroidal transmission unit 20 are symmetrically arranged with respect to the central axis c, and the respective power rollers 18c, 18d, 20c and 20d are tilted (tilted) according to vehicle operating conditions via a shift control valve 60 as a shift control device and hydraulic cylinder devices 50, 52, 54 and 56, and thus the first and second input disks The rotation of the rotation of 18a, 20a is steplessly transmitted to the first and second output disks 18b, 20b.
[0021]
That is, as shown in FIGS. 2 and 3, the power rollers 18c, 18d and 20c, 20d are hydraulic cylinder devices 50, 52, 54 provided corresponding to the respective power rollers 18c, 18d, 20c, 20d. , 56, which are rotatably mounted via pivot shafts 50b, 52b, 54b, 56b to trunnions 50a, 52a, 54a, 56a which are vertically moved by the trunnions 50a, 52a, 54a, 56a. Thereby, the power rollers 18c, 18d and 20c, 20d can be tilted.
[0022]
Accordingly, the amount of tilt of the power rollers 18c, 18d and 20c, 20d, that is, the amount of rotation of the trunnions 50a, 52a, 54a, 56a is determined by the amount of operation of the hydraulic cylinder devices 50, 52, 54, 56. Will be.
[0023]
Here, the shift control of the present invention will be described with reference to FIG.
The shift control valve 60 includes a rod 62 and a sleeve 63 driven by a step motor 61, a spool 64 inserted into the inner diameter of the sleeve 63, and a spring 65 for pressing the spool 64 in a direction opposite to the step motor 61. It has. The spool 65 always presses the spool 64 against the link 67a, so that mechanical feedback reliably works.
[0024]
On the contrary, since the spring 65 expands and contracts in accordance with the movement of the spool 64, the movement of the spool 64, that is, the tilt angle of the trunnions 50a, 52a, 54a and 56a and the amount of displacement corresponding to the axial displacement amount. The force is exerted on the trunnions 50a, 52a, 54a, 56a through the precess cam 67 and the link 67a.
An axial groove is formed on the outer circumference of the sleeve 63, and a pin is engaged with the groove so that the sleeve 63 can move in the axial direction without being rotated.
The rotation amount and the axial movement amount of one of the trunnions 50a, 52a, 54a, and 56a are provided at the end of the spool 64 opposite to the side on which the spring 65 is provided by the precess cam 67 and the link 67a. Is converted into an axial movement amount, and this axial movement amount is introduced as a feedback amount.
That is, the amount of rotation of the trunnions 50a, 52a, 54a, 56a is proportional to the amount of tilt of the power rollers 18c, 18d and 20c, 20d, and feeding back the amount of rotation of the trunnions is performed by the power roller 18c. , 18d and 20c, 20d.
[0025]
The line pressure generated by the hydraulic pump 69 is introduced from the introduction port 68 to the shift control valve 60, and the line pressure is applied to the first port 68a or the second port 68b depending on the relative positional relationship between the sleeve 63 and the spool 64. Supplied.
[0026]
The line pressure from the first port 68a and the second port 68b is supplied to the hydraulic cylinder devices 50, 52, 54, and 56 to the pipelines 70a, 70b, 72a, 72b, 74a, 74b, 76a, 76b, Is supplied via In the hydraulic cylinder devices 50, 52, 54 and 56, the upper chamber A and the lower chamber B are separated by pistons 50c, 52c, 54c and 56c, respectively, and a higher oil pressure is supplied to the upper chamber A than to the lower chamber B. Accordingly, the respective trunnions 50a, 52a, 54a, 56a are moved downward, and conversely, a higher hydraulic pressure is supplied to the lower chamber B than to the upper chamber A, whereby the respective trunnions 50a, 52a, 54a and 56a are moved upward.
[0027]
On the other hand, the hydraulic cylinder devices 50 and 52 of the first toroidal transmission unit 18 and the hydraulic cylinder devices 54 and 56 of the second toroidal transmission unit 20 respectively include one upper chamber A, the other lower chamber B, and one lower chamber B. The other upper chamber A crosses and communicates with each other, so that the hydraulic cylinder devices 50 and 54 and the hydraulic cylinder devices 52 and 56 are operated in directions opposite to each other.
[0028]
The upper chamber A of the hydraulic cylinder devices 50 and 54 and the lower chamber B of the hydraulic cylinder devices 52 and 56 are connected to the first port 68a of the shift control valve 60, and the lower chambers B and 52 of the hydraulic cylinder devices 50 and 54 are connected. , 56 are connected to the second port 68b of the shift control valve 60.
[0029]
Now, it is assumed that the rotation amount and the axial movement amount of the trunnion 50a are converted into the axial movement amount via the precess cam 67 and the link 67a to change the position of the spool 64. At the time of steady operation, the sum of the traction force of the power roller 18c from the input disk 18a and the reaction force of the traction force from the power roller 18c to the output disk 18b is the differential pressure generated by the hydraulic cylinder device 50 and the reaction force of the spring 65. Will be balanced with the total value of 1.
[0030]
Preload canceling means (reaction force compensating means) 82, 84, 86 for generating a force equivalent to the force generated by the spring 65 according to the tilt angle and the axial displacement in the remaining trunnions 52a, 54a, 56a. The total value of the traction force from each of the power rollers 18d, 20c, 20d is determined by the differential pressure generated by the corresponding hydraulic cylinder device 52, 54, 56 and the pre-pressure canceling means 82, 84, 86, respectively. And the total value 2 of the forces from.
[0031]
Since the force exerted on the trunnion 50a by the spring 65 and the force exerted by the preload canceling means 82, 84, 86 on the trunnions 52a, 54a, 56a are always equal irrespective of the tilting motion and the axial displacement, the total value is 1 And the sum 2 is also equal. Therefore, the traction forces to be balanced are all equal, and as a result, the torque sharing is equal.
[0032]
Next, the preload canceling means 82, 84, 86 will be described with reference to FIGS. 2, 3A, 3B, and 3C.
In this embodiment, the pre-pressure canceling means 82, 84, 86 are installed in hydraulic cylinder devices 52, 54, 56. The preload canceling means 82, 84 and 86 are composed of a plate spring 90, a stopper 91 for fixing the plate spring 90 at a predetermined position, and a slope 92 provided on the pistons 52c and (54c and 56c). ing.
[0033]
The angles of the slopes 92 provided on the pistons 52c, (54c, 56c) are set so that the ratio and the amount of feedback to the spool 64 by the precess cam 67 and the link 67a are equal. That is, assuming that the link ratio is 2, the angle of the slope 92 is の of the slope of the precess cam 67. At this time, the spring constant of the plate spring 90 is equal to that of the spring 65.
[0034]
Here, the portion where the plate spring 90 comes into contact with the pistons 52c, (54c, 56c) is processed into a circular shape (spherical shape) as shown in FIG. 3B, and the trunnions 52a, 54a, 56a are processed. A device is devised to minimize the friction at the contact portion with the pistons 52c, (54c, 56c) that rotate integrally with the tilting motion. If this friction is not reduced, only the friction in the tilt direction of the trunnion 50a connected to the precess cam 67 is small, and the remaining friction in the tilt direction of the trunnions 52a, 54a, 56a is large. Will appear as a difference.
[0035]
The plate spring 90 is fixed by a stopper 91 at a position where the spring 65 can generate a force equivalent to the force exerted on the trunnion 50a when the gear ratio is the lowest. Thereafter, since the plate spring 90 has the above-described characteristics, the spring 65 is always generated even if the trunnions 52a, 54a, 56a make a tilting motion or displace in the axial direction. An equivalent force is generated to exert a force on each of the trunnions 52a, 54a, 56a.
[0036]
(Other embodiments)
In the above embodiment, since the preload canceling means 82, 84, 86 are provided for the remaining trunnions 52a, 54a, 56a other than the trunnion 50a connected to the precess cam 67, for example, When four power rollers are provided, it is necessary to provide three preload canceling means.
This is the second embodiment.
In the second embodiment, a pre-pressure canceling means having a configuration for canceling a reaction force from the spring 65 is provided. Therefore, there is an advantage that it is necessary to install only on the trunnion 50a connected to the precess cam 67.
As a function of the preload canceling means in the second embodiment, the opposite force to the spring is required, in which the attraction force is weaker as the distance increases and the attraction force increases as the distance increases. Then, the characteristic is realized using magnetic force. As is well known, the magnetic force acts with a strength inversely proportional to the square of the distance, and its characteristics are, for example, as shown in FIG.
[0037]
The details of the second embodiment will be described with reference to FIGS.
In FIG. 4, reference numeral 100 denotes a magnet as preload canceling means, and 101 denotes an iron core. The magnet 100 is fixed to a CVT case. The iron core 101 is installed on the trunnion 50a connected to the precess cam 67, and has a structure in which a force is applied to the trunnion 50a by attracting the magnet 100.
[0038]
The iron core 101 moves in the axial direction as the trunnion 50a is displaced in the axial direction. At the same time, the iron core 101 has a slope as shown in FIG. The structure is such that the distance L from the center of the magnet 100 changes continuously and the attraction force changes. Here, the inclination of the inclined surface of the iron core 101 is set to an amount that is equal to the ratio of the amount of tilting of the amount fed back to the spool 64 by the precess cam 67 and the amount of axial displacement (that is, the initial amount). Same as the embodiment).
[0039]
The relationship between the reaction force from the spring 65 and the magnitude of the force received by the magnetic force has, for example, characteristics as shown in FIG. That is, as the reaction force of the spring 65 changes in a linear relationship in accordance with the axial displacement amount, the magnetic force changes in a relationship that is almost proportional to the spring force, which is inversely proportional to the square of the distance, and the direction of the force is opposite. Orientation.
[0040]
With this setting, the total value of the external forces acting on the trunnion 50a is not only substantially constant at all times, but also the magnitude of the force is smaller than when only the force from the spring 65 acts. It is possible to reduce the non-uniformity of the torque sharing ratio (the magnetic force characteristic is originally non-linear, and the distance between the magnet 100 and the iron core 101 changes in both the axial direction and the tilting direction, so that the configuration is completely canceled. Is not possible.).
[0041]
As the structure of the iron core 101, FIGS. 5B and 5C can be considered in addition to FIG. 5A.
The example of FIG. 5B is an example in which a step is provided instead of having a slope.
The structure is such that the distance between the magnet 100a and the iron core 101a is L1 and L2 at the step 102a. If it is tilted clockwise, the area where the shorter distance is opposed to the magnet 100a increases, and the magnitude of the acting force increases. If it tilts counterclockwise, the area decreases, and the magnitude of the acting force It also reduces. That is, with the tilting motion, the area ratio between the portion where the distance between the magnet 100a and the iron core 101a is short and the portion where the distance is far changes, and a force corresponding to the tilt angle can be generated.
[0042]
FIG. 5C shows an example in which the magnets 100b and 100c are provided at two places with the trunnion 50a interposed therebetween.
The iron core 101b is integrally formed in an annular shape, and is formed so that steps 102b and 103b come on each magnet (when considering the direction of the steps, the iron core 101b has four steps. , Two of which 102b, 103b are on the magnet).
Further, an annular iron material 104 is provided below the magnets 100b and 100c. The installation of the annular iron material 104 and the integration of the iron core 101b serve to increase the magnetic force by creating a path through which magnetic flux can easily pass. In the case of this configuration, it is desirable that the magnets 100b and 100c have an S pole and an N pole on the front and back, for example, as shown in the drawing.
[0043]
As described above, the toroidal type continuously variable transmission of the present invention employs the above-described structure, so that the transmission torque can be equalized without deteriorating the efficiency of the transmission. The effect that can be obtained is obtained.
[Brief description of the drawings]
FIG. 1 is a system diagram showing one embodiment of the present invention.
FIG. 2 is a system diagram showing a cross section of one embodiment of the present invention.
FIG. 3 is a detailed view showing a part viewed from an arrow Z in FIG. 2;
FIG. 4 is a system diagram showing a cross section of the second embodiment of the present invention.
FIG. 5 is a detailed view showing a second embodiment of the present invention.
FIG. 6 is a characteristic diagram showing a pressing force.
FIG. 7 is an explanatory diagram showing a force relationship according to the second embodiment.
[Explanation of symbols]
10 Toroidal type continuously variable transmission
18 First toroidal type continuously variable transmission
20 Second toroidal type continuously variable transmission
18a First input disk
18b First output disk
20a Second input disk
20b Second output disk
18c, 18d Power roller
20c, 20d Power roller
34 Loading cam device
38 Disc spring
50, 52 Hydraulic cylinder device
54, 56 Hydraulic cylinder device
50a, 52a, 54a, 56a Trunnion (power roller support member)
60 Shift control valve
61 Step motor (actuator)
63 sleeve (shift control valve)
64 spool (shift control valve)
65 Spring (shift control valve)
67 Precess cam
67a link
82, 84, 86 pre-pressure canceling means
90 leaf spring (preload canceling means)
92 Slope (Preload canceling means)
100, 100a magnet (preload canceling means)
100b, 100b 'magnet (preload canceling means)
101, 101a, 101b Iron core (preload canceling means)
102a, 102b, 103b step (preload canceling means)

Claims (6)

From the input disk, an output disk coaxially arranged with this, a plurality of power rollers pressed against the opposing surfaces of these disks, and a power capable of rotatably supporting the power rollers and capable of tilting movement and capable of vertical displacement. A toroidal-type continuously variable transmission having a roller support member and a hydraulic cylinder device for vertically displacing the power roller support member,
A shift control valve for controlling the hydraulic pressure of the hydraulic cylinder device; the shift control valve has a sleeve and a spool fitted in a state in which the shift control valve can move relative to each other; one of the sleeve and the spool is a target to be commanded; The position is determined according to the tilt angle, the actuator is used for the displacement, and the position is determined according to the actual tilt angle of the power roller support member, and the cam mechanism is used for the displacement. In a toroidal-type continuously variable transmission having a preload mechanism for ensuring transmission of displacement to a shift control valve,
A preload canceling means for generating a force equivalent to the preload mechanism is provided for a power roller supporting member without a cam mechanism, and the preload canceling means reduces friction in the tilt direction due to the installation of the preload mechanism. A toroidal-type continuously variable transmission characterized by having means for: From the input disk, an output disk coaxially arranged with this, a plurality of power rollers pressed against the opposing surfaces of these disks, and a power capable of rotatably supporting the power rollers and capable of tilting movement and capable of vertical displacement. A toroidal-type continuously variable transmission having a roller support member and a hydraulic cylinder device for vertically displacing the power roller support member,
A shift control valve for controlling the hydraulic pressure of the hydraulic cylinder device; the shift control valve has a sleeve and a spool fitted in a state in which the shift control valve can move relative to each other; one of the sleeve and the spool is a target to be commanded; The position is determined according to the tilt angle, the actuator is used for the displacement, and the position is determined according to the actual tilt angle of the power roller support member, and the cam mechanism is used for the displacement. In a toroidal-type continuously variable transmission having a preload mechanism for ensuring transmission of displacement to a shift control valve,
For a power roller supporting member without a cam mechanism, a preload canceling means for generating a force equivalent to the preload mechanism is provided, and the preload canceling means has a slope equivalent to the cam mechanism in a tilt direction. A toroidal-type continuously variable transmission characterized in that the ratio of the inclination of the slope to the amount of vertical displacement is set to be equal to that of the cam mechanism, and the spring is extended and contracted by the slope. From the input disk, an output disk coaxially arranged with this, a plurality of power rollers pressed against the opposing surfaces of these disks, and a power capable of rotatably supporting the power rollers and capable of tilting movement and capable of vertical displacement. A toroidal-type continuously variable transmission having a roller support member and a hydraulic cylinder device for vertically displacing the power roller support member,
A shift control valve for controlling the hydraulic pressure of the hydraulic cylinder device; the shift control valve has a sleeve and a spool fitted in a state in which the shift control valve can move relative to each other; one of the sleeve and the spool is a target to be commanded; The position is determined according to the tilt angle, the actuator is used for the displacement, and the position is determined according to the actual tilt angle of the power roller support member, and the cam mechanism is used for the displacement. In a toroidal-type continuously variable transmission having a preload mechanism for ensuring transmission of displacement to a shift control valve,
A preload canceling means for generating a force equivalent to the preload mechanism is provided for a power roller supporting member without a cam mechanism, and the preload canceling means is composed of a magnet and an iron core having a slope or a step. A continuously variable toroidal transmission. From the input disk, an output disk coaxially arranged with this, a plurality of power rollers pressed against the opposing surfaces of these disks, and a power capable of rotatably supporting the power rollers and capable of tilting movement and capable of vertical displacement. A toroidal-type continuously variable transmission having a roller support member and a hydraulic cylinder device for vertically displacing the power roller support member,
A shift control valve for controlling the hydraulic pressure of the hydraulic cylinder device; the shift control valve has a sleeve and a spool fitted in a state in which the shift control valve can move relative to each other; one of the sleeve and the spool is a target to be commanded; The position is determined according to the tilt angle, the actuator is used for the displacement, and the position is determined according to the actual tilt angle of the power roller support member, and the cam mechanism is used for the displacement. In a toroidal-type continuously variable transmission having a preload mechanism for ensuring transmission of displacement to a shift control valve,
Tilting to the power roller supporting member marked with a cam mechanism, by installation of the only setting a preload force canceling means for applying a force in a direction to cancel it with preload mechanism equivalent,該予pressure canceling means preload mechanism A toroidal-type continuously variable transmission having means for reducing directional friction. From the input disk, an output disk coaxially arranged with this, a plurality of power rollers pressed against the opposing surfaces of these disks, and a power capable of rotatably supporting the power rollers and capable of tilting movement and capable of vertical displacement. A toroidal-type continuously variable transmission having a roller support member and a hydraulic cylinder device for vertically displacing the power roller support member,
A shift control valve for controlling the hydraulic pressure of the hydraulic cylinder device; the shift control valve has a sleeve and a spool fitted in a state in which the shift control valve can move relative to each other; one of the sleeve and the spool is a target to be commanded; The position is determined according to the tilt angle, the actuator is used for the displacement, and the position is determined according to the actual tilt angle of the power roller support member, and the cam mechanism is used for the displacement. In the toroidal-type continuously variable transmission having a preload mechanism for ensuring transmission of the displacement to the shift control valve,
A preload canceling means is provided for applying a force to the power roller supporting member having a cam mechanism in a direction equivalent to the preload mechanism and canceling the preload mechanism. The preload canceling means tilts a slope equivalent to the cam mechanism. The toroidal stepless step has a structure in which the inclination of the slope and the amount of vertical displacement are set to be equal to that of the cam mechanism, and the spring is extended and contracted by the slope. transmission. From the input disk, an output disk coaxially arranged with this, a plurality of power rollers pressed against the opposing surfaces of these disks, and a power capable of rotatably supporting the power rollers and capable of tilting movement and capable of vertical displacement. A toroidal-type continuously variable transmission having a roller support member and a hydraulic cylinder device for vertically displacing the power roller support member,
A shift control valve for controlling the hydraulic pressure of the hydraulic cylinder device; the shift control valve has a sleeve and a spool fitted in a state in which the shift control valve can move relative to each other; one of the sleeve and the spool is a target to be commanded; The position is determined according to the tilt angle, the actuator is used for the displacement, and the position is determined according to the actual tilt angle of the power roller support member, and the cam mechanism is used for the displacement. In the toroidal-type continuously variable transmission having a preload mechanism for ensuring transmission of the displacement to the shift control valve,
The power roller supporting member having the cam mechanism is provided with a preload canceling means for applying a force in a direction equivalent to the preloading mechanism to cancel the same, and the preloading canceling means includes a magnet, a slope or a step. A toroidal-type continuously variable transmission comprising an iron core.

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